Automatic lubricating systems for shafts



May 1, 1956 w. BORBERG 2,743,788

AUTOMATIC LUBRICATING SYSTEMS FOR SHAFTS Original Filed Nov. 25, 1949 3 Sheets-Sheet l W/LL Y 3028506 Gnome May 1,, 1956 w. BORBERG AUTOMATIC LUBRICATING SYSTEMS FOR SHAFTS 5 Sheets-Sheet 2 Original Filed NOV. 25, 1949 MAL Y 8091954 6,

Jnuento'r Gltorneu May 1, 1956 W BQQBERG 2,743,788

AUTOMATIC LUBRICATING SYSTEMS FOR SHAFTS Original Filed Nov. 25, 1949 3 Sheets-Sheet 3 I [:1 E x g a "h ""ll W/LL Y 301M596 JNVENTOR.

United States Patent AUTOMATIC LUBRICATING SYSTEMS FDR SHAFTS Willy Borberg, North White Plains, N. Y., assignor to International Projector Corporation, Bloomfield, N. 5., a corporation of Delaware Claims. (Cl. 184--6) This invention relates to improvements in automatic lubricating systems for shafts, and more particularly to the provision of a closed circuit, lubricating system for automatically inducing a circulation of lubricant through such system, the lubricant being drawn from a suitable supply, and returned to the supply for re-circulation. While the invention is particularly designed for the automatic lubrication of the enclosed intermittent movements of motion picture projecting machines, and for preventing seepage of the lubricant onto the film-carrying parts of the projector, its use is by no means confined to such machines.

This application is a divisional part of my parent application Serial No. 129,315, filed in the United States Patent Office November 25, 1949, now Patent Number 2,689,021.

. Special provision is made to supply the enclosed intermittent movement parts with an adequate amount of oil. These enclosed parts include, in the present illustration of the invention, a cam and star wheel of the typical Geneva movement, although it is to be understood that other forms of intermittent film feed mechanisms such as that shown in U. S. patent to Nicolas Power, No. 1,129,121, issued February 23, 1915, could be substituted for the form herein illustrated without departing from the invention.

The quality of the picture projection as far as screen image-steadiness is concerned, depends mainly upon the accurate functioning of the intermittent movement, which operates to pull the film down intermittently at a normal rate of 24 frames per second.

It must be realized that the pull-down time at the stated rate amounts to but of a second, and that at this speed, the weights and sizes of the intermittently operating parts should be held to the minimum consistent with strength.

These requirements necessitate the location of the intermittent housing in close proximity to the fim center line to obtain a short shaft of low mass for coupling the intermittent film feeding sprocket with its intermittent mechanism, as a Geneva star wheel, or a fin-cross of the Powers patent, above referred to.

The provision of a short coupling shaft requires the location of the housing enclosing the intermittent driving parts as close to the center line of the film as possible. In the present instance, the housing is located inside the main frame partition separating the film compartment from the mechanism compartment which latter compartment, during the operation of the machine, is constantly sprayed with lubricant, the short coupling shaft with its sprocket extending into the dry film compartment.

Obviously, the lubricant falling by gravity in the Wet mechanism compartment would not readily find its Way into the chamber of the housing enclosing the intermittent drive mechanism, and this difiiculty is increased when the projector is tilted downwardly, say 35 degrees from the horizontal, or upwardly, say, degrees from the horizontal. Such a tilting results in shifting the location of 2,743,788 l atented May 1, 1956 the oil receiving holes for catching the vertically dripping lubricant, when the projector is in its horizontal position, to a location wherein the oil receiving holes lie at an angle to the vertically dripping oil, the paths of which oil droplets are displaced from those followed when the projector is in its horizontal position.

Also, the problem heretofore encountered, of supplying lubricant to the intermittent chamber in any operating position is further complicated by the requirement that the intermittent housing be free for rocking adjustment through a degree are in film framing operations.

Hence it will be seen that, due to the fact that the closed chamber in which the effective elements of the intermittent mechanism are located, is itself enclosed within the partition separating the wet and dry sides of the projector head, and also in view of the necessity for rotating the intermittent mechanism in film framing operations, the gravity drenching lubricating methods of the prior art cannot be relied upon to provide a supply of oil for a closed circulatory oiling system throughthe intermittent movement.

Therefore, one object of this invention is the provision of an automatic force feed circulatory lubrication system for the intermittent movement.

A co-related object is the provision of a force feed Inbricating system which is contained within the intermittent movement itself so as to be capable of efiicient operation in any position to which the intermittent movement may be adjusted.

It is quite essential that the operating side of the projector head through which the film travels, be dry, that is, that no lubricant be permitted to leak from the intermittent movement housing along the star wheel shaft to the intermittent feed sprocket, with a possibility of contact with the film.

Another object of the invention, therefore, is the pro vision of means to automatically prevent leakage of lubricant to the intermittent sprocket which means, operating in a novel manner, utilizes the suction pump principle.

Still another object is to provide means to automatically maintain a correct oil level in the intermittent chamher and to drain excess lubricant into the sump or reservoir regardless of the tilt or position to which the machine and the intermittent movement may be adjusted.

The effective elements of the intermittent movement, as for instance, the star wheel and cam, as Well as the intermittent shaft bearing are critical parts and require the utmost precision in manufacture to act under extremely close tolerances. Any undesirable substances should be excluded from the compartment housing the intermittent movement.

Hence, a still further object of this invention is the provision of a filter capable of removing very fine particles from the oil as it is forced through the closed circulatory system for the intermittent movement.

Other objects and advantages will be more clearly disclosed in the following specification and particularly pointed out in the claims. 1

In the accompanying drawings,

Fig. l is a side view of the non-operating side of a motion picture projecting machine of the Simplex type, to which the present invention is applied, parts having no relation to the invention disclosed being omitted;

Fig. 2 is an enlarged detail view in horizontal crosssection taken on line 2--2 of Fig. 4, showing the intermittent mechanism, and the self-contained lubricating system therefor;

Fig. 3 is a detail end view of the inner bearing of the intermittent drive shaft, showing the arrangement of the excess oil discharge outlets;

Fig. 4 is a detail end view taken on the line 4--4 of jection head is formed with an oppositely flanged circular opening 60 (Fig. 2) constituting a bearing for a circular cam ring 61 having an eccentrically located bore 62 to accommodate the cylindrical casing head 50 to which the circular cam ring is secured, the casing head being chambered at its inner end at 64, and having at its outer end a projecting arm 65 arcuate in cross-section, connecting the cylindrical casing 50 with a bearing yoke 66 eccentric to the chambered casing, as shown in Fig. 1. A jack or drive shaft 67 is journaled in bearings 68, 69 mounted in seats 70 and 71 in the head ofthe cylindric casing and in the bearing yoke 66, respectively, the axial centers of the bearings 68, 69 and the jack shaft 67 lying in line with the longitudinal center of the bearing ring 61. A second set of bearings 72, 73 are seated in alined holes in the head of the cylindrical casing 50 and in the bearing yoke 66,respectively, and are spaced radially apart from their companion bearing seats 70 and 71, to support at Geneva cam shaft or intermediate shaft 74- for rotation in intermittent film feeding.

In framing operations, rocking the bearing casing 50 with its connected bearing yoke 66 and cam ring 61 in the bearing 60 about the longitudinal axis of the jack shaft 67 as a center, will cause the cam shaft 74 to travel bodily about the jack shaft.

The inner end of the cam shaft 74 protrudes into the closed chamber 64 at the inner end of the casing head 50 and carries the well known Geneva cam 75 and crank pin 76. A cover plate 77 closes the open end ofthe chamber 64 and is provided with an eccentrically located hub 78 extending into the operating chamber of the projector head and bored in exact alinement with the longitudinal axis of the jack shaft 67 to accommodate a sleeve bearing '79 for the star wheel shaft 80. The star wheel or drive shaft protrudes beyond the inner end of its bearing into the chamber64 through the cover plate 77 and carries the usual Geneva star wheel 81 in position to be alternately engaged by the crank pin 76 and by the cam 75 on the cam shaft 74. The intermittent film feed sprocket 82 is fast on the outer end of the star wheel shaft, said extreme outer end of the star wheel shaft being supported in a bearing 83 at the outer end of a bracket arm 84 projecting from the cover plate 77.

Recalling that rotation of the casing head 50 eccentrically about the longitudinal axis of the jack shaft 67 indicated by the dot-and-dash center line X-X, Fig. 2, bodily revolves the cam shaft 74 about the jack shaft, and that the star wheel shaft 80 is in exact longitudinal alinement with the jack shaft, it is clear that such bodily rocking of the cam shaft will shift the Geneva cam 75 and pin 76 on the cam shaft relatively to the Geneva star wheel 81 whereby to position the film frames in register with the projection aperture, in a manner well known in the art as framing.

A gear 85 on the vertical counter-shaft 14 meshes with a driven gear 86 on the jack shaft 67 to drive the latter, the outer end of this jack shaft projecting beyond the outer face of the bearing yoke 66 and having fast thereon a helically toothed gear 87 engaging a complementary toothed gear 88 fast on the outwardly extended end of the cam or intermediate shaft 74, whereby during the operation of the machine, continuous rotation is imparted to the cam shaft with its cam and crank pin, to advance the star wheel 81 intermittently step by step with its shaft 00 and intermittent sprocket 82.

Turning a framing knob 90 (Fig. 1) in one direction or the other operates through a train including a gear 91 meshing with an arcuate rack 92 mounted on the eccentric ring 61, to swing the casing head 50, 65, 66 and its cover plate 77 and arm 84, and the cam shaft 74 bodily relatively around the center line X-X to advance or retard the film for framing purposes, as it also well known in the art.

The novel self-contained power driven lubricating system is applied to the above described intermittent move': ment as follows:

Referring to Fig. 1, a wide-mouthed funnel mounted in the non-operating chamber adjacent and on a plane slightly below the centrifugal governor, but preferably out of the path of lubricant discharged from the outlet tube 49, traps a part of the oil diffused by the governor, which trapped lubricant is discharged onto the intermeshing helical gears 87, 88 through a supply pipe 101 leading from the restricted end of the funnel to a point between the customary flywheel 89 on the outer end of the cam shaft 74, and the outer face: of the bearing yoke 66.

By partially housing the intermeshed helical gears in a cradle 102, best shown in Figs. 1 and 4, having pockets conforming with the peripheries of the helical gears, the latter acquire a dual function, that is, they retain their accustomed character as power transmitters, and in addition, are enabled to perform as a fluid pump.

The cradle 102 is secured to the outer face of the bearing yoke 66 to turn therewith in framing operations, the cradle being of a width (see Fig. 2) approximately equal to the distance between the outer face of the bearing yoke 66 and the inner face of the flywheel 89, which faces, with the cradle, form a container (see Figs. 1 and 4) for the lubricant discharged onto the helical gears from the supply pipe 101.

The bearing yoke 66 has drilled therein a supply duct 103 leading from a point above the bottom of the cradle and closely adjacent the point at which the intermeshing teeth of the combined power transmitting gears and pump first engage, the duct leading to the inner end of a filtering cell 104 at one side of a filtering material 105 (Fig. 4) contained in the cell, an outlet duct 106 leading from the filtering cell above the filtering material and through the arcuate arm 65 to the closed intermittent chamber 64 in the casing head 50 into which it discharges. A removable closure 107 for the cell 104 permits inspection, cleaning, and removal and substitution of the filtering material when necessary. These ducts 103, 106 might well be in the form of tubes arranged exteriorly of, and carried by, the bearing yoke 66, arm 65, and easing head 50, but such arrangement would expose the tubes to the liability of damage, which is avoided by drilling the ducts in the casting itself.

From the foregoing, it is seen that when the machine is in operation, the intermeshing helical gears 87, 88 in the pocketed cradle 102 serve as a pump to drive the fluid lubricant along the supply duct 103 under suflicient pressure to force the lubricant through the filter 105 and through the outlet duct 106 from whence it is discharged into the closed chamber 64 housing the Geneva gearing, where it collects and rises to a height sufficient to submerge the lower slotted teeth of the star wheel 81. The star wheel, intermittently rotating at the usual average rate of 360 revolutions a minute, has a momentary maximum speed of about 3500 revolutions per minute during the turn-over only, it being remembered that a fourtoothed star wheel turns only one-quarter of a revolution at a time, so that during that quarter-turn it has to make up in speed for the time it remains at rest.

At such R. P. M. the star wheel imparts a high degree of turbulence to the pool of lubricant in the closed intermittent movement chamber 64, resulting in drenching the entire movement with oil. The star wheel 81 and its shaft 80 are axially drilled, as at 108, the inner end of the passage opening on the face of the star wheel, being enlarged (see Figs. 2, 6, and 7) to form an oil intake and the outer end of the passage terminating in a radial outlet 109 (see Figs. 2 and 8) leading to the periphery of the star wheel shaft at a point Within the bearing sleeve 79. The oil or other suitable lubricant fills the enlarged open end of the axial oil passage 108 in the star wheel, and is drawn into the axial passage 108 due in part to capillary attraction and in part to the suction created'at the outer end of the passage owing to the rapid rotation of the star wheel shaft fifi and its radially extendingoutlet 'l09, as has-been proven bytests. Thellubrieant thusdrawn into the oil passage 103 is dischargedihroughtthe outlet 109 where it spreads between the star-wheel shaftandits sleeve bearing and is returned along .theshaft towards the closed intermittent movementxchamber throughthe .usualspiral oil return groove 1 (Fig-8): cut peripherally into the shaft, or .if preferred, .-:the.- spiral .groove may be cut zinternally of the sleeve :bearing.

2However, inotwithstanding the action of the return groove, the flow of oil from the outlet 109 is socopious that some of ;it.might.escape fromthe outer endof the sleeve bearing and 'be thrown on the .film as it is fed by:.the :intermittentsprocket .82 located adj acentthe outer end ;of the sleeve ,b'earing. To prevent such undesirable result,.a furtherdevelopment of this invention includes the provision of '.-means to insure the return of lubricant from betweenthe starwheel shaft 80 and its sleeve bearing .79 to the closed intermittent movement chamber 64 thus forming a complete circuit for the lubricant. To this ,end, a circular collar orenlargement 111 .(see vFigs. 5 -7) is provided :between .the .star wheel and its shaft within "the closed chamber .64, the collar preferably being ofgreater diameter .than, and integral with, the shaft. An annular collecting groove 112, best shown in Figs. 5, '6, and '7, at .the juncture of the shaft 80 and the outer faceof its collar :111, ,is :formed .partly in the shaft and partly .in the adjacent face of the collar. 'The inner end .ofthe spiral-oilreturn.groove110 communicates with that portion of the annular collecting groove or chamber 112 formed. in the star wheel .shaft, to which it delivers the oil fromthe'bearingsleeve'79and star wheel shaft. The

outer face of the circular collar 111, which fits snugly against theinnerend of the sleeve bearing '79, is provided withoutwardlyextendingZflutes or ports 113 leading from the annular collecting groove, which flutes may be radial, as shown in Figs. 2 and 6, tangential, as shown in I Fig-5,0 1 radially inclined, as shown in Fig. 7. The flutes or ports with collarlll, rotating with the star .wheel 80, set-up a suction by centrifugal action to withdraw the oil from the collector groove 112 and from the star wheel shaft bearing, .and disperse it from the flutes around the intermittent movement chamber 64. This suction .return of :the lubricant to the intermittent chamber constitutes one of be several novel features of this invention, and is 'effectiveto prevent leakage oflubricant from the front end ofthe rstar wheel shaft bearing 79 onto the intermittentrfeed ,sprocketand the film engaging the sprocket.

Ioprevent ;the intermittent chamber 64 from becoming' filled with 'oil, it has been customary to provide a drain opening drilled through the wall of the chamber to discharge excess ,oil from the intermittent chamber into the sump, but this discharge was only effective when the intermittent movement was rotated within a comparatively restricted part of themaximum angle which the intermittent movement might assume, not alone in framing operations forwhichan'adjustment of 90 is usually provided, .but also through the tilting adjustment of the entire machine forwardly or rearwardly from a horizontal plane, such tilting adjustment adding another 60 more or less to the range of positions which the intermittent movement may have to. assume.

To'provide a universal means to maintain the liquid level at a reasonable height irrespective of the angular relation of the intermittent movement to the horizontal, the bearing 68 (Figs. 2 and 3) for the inner end of the jack shaft 67 is extended through one wall of the bearing casing enclosing the intermittent chamber 64 at a point above the bottom of the chamber, the bearing 68 being peripherally'grooved, as at 1-14 (Figs. 2 and 3) substantially throughout its circumference to drain-the chamber to the level of whichever groove is the lowest in any of the possible angular positions of the intermittent movement.

Obviously, .rotatiomofithe intermittent movement in framing vand gin ztiltingzthe machine will also affect the relation ofthe sintermittent movement to the oil supply pipe 101. :InFigA,.theintermittent movement is shown in one of .aznumber.of'itspossible angular positions, in any OfWhiChZthG universalarrangement of drain grooves will preventuthe oil rlevel intheintermittent chamber from rising too-high, .and-theoil supply pipe 101, because of the location of itsdischarge endnear the center of bodily rotationcf .the intermittent movement, will deliver oil ontooneor the other oflthevhelicalgears 87, 88 of the combined .intermittentxdrive andpump in any position which the intermittent movement ,is likely to assume in use.

:Fromthe foregoing itiiS clear that the invention contemplates theprovision ofanadequate system of lubrication for ;the driving ,mechanism of the projector head, wherein .the 'welhknown governor, heretofore employed only as ,a:means:for .controllingthe operation of a safety part accordinglyasxthe speed of rotation of the drive mechanism increases above-or decreases below a predetermined .numbenof revolutions, is. given the additional function of disseminating the lubricant in droplets throughout the non-operating side of the projector head to coverallexposed.partsof the driving mechanism.

.''Furthermore, a circulatory lubricating system is provided for the enclosed intermittent-movement, which system, -in.the therein :illustrated .form of the invention, is supplied'withllubricant distributed by the governor, and the supply .is so contrived. as to deliver lubricant to the intermittent movementin any position that the intermittent movement may aBSSlJIIlfi in framing. 1

In this circulatory system also, the usual intermeshing gears aheretofore .used .solely for imparting continuous rotation to the cam shaftof the intermittent movement are given the additional function of performing as a fluid gear pump to supply lubricant to the chamber in the intermittent movementcasinghead or housing.

Also, the lubricant is maintained at a constant level in the casing .headzchamber in.;any position to which the intermittent movement may ,rock in the framing operations, it being seen that the circular arrangement of over- .flow apertures equidistant from the axis of rotation of the intermittent-movement in framing operations eflects this result.

Lastly, there ,is provided the closed circulatory automatic lubricating system for the sprocket shaft which-derives .its supply of oil from .the closed chamber of the intermittent movement to which the oil is fed by the dual purpose driving and fluid pump, gears.

Changesother than those hereinbefore-referred to may be made in -the form and arrangementof the several parts described Without departing from the spirit and scope of the invention asset forth in the appended claims.

What I claim as new is: r

1. In alubricating system, the combination with a shaft, having means formed interiorly thereof to draw lubricant from a supply and discharge it at the periphery of :the shaft ata point remote from the supply; and means formed peripherally of the shaft to return the lubricant .towards the supply; .of a collecting means comprising a groove formed circumferentially of the shaft; a collar rotatable with the shaft, said collar having a radial jet opening communicating with the lubricant collecting groove to draw the lubricant therefrom and return it to the supply.

2. A closed circuit lubricating means for shafts, including, in combination with a casing having a chamber; means to supply lubricant to the chamber; and a rotary shaft, one end of'which projectsinto the lubricant chamber; means to lead lubricant from the chamber through the shaft :and discharge .it-xat .the periphery of the shaft at a point remote from the lubricant chamber; a lubricant conductor arranged spirally of the shaft from the point which the lubricant is discharged at the periphery of the shaft back toward the lubricant chamber; and suction means communicating with the free end of the spiral conductor to create a partial vacuum in the spiral conductor to induce a flow of lubricant along the spiral conductor, and to return the lubricant to the chamber for re-circulation.

3. In a lubricant circulating system for shafts, the combination with a casing having a chamber; means to supply the chamber with lubricant; a rotary shaft, one end of which projects into the lubricant chamber; lubricantconducting means leading from the chamber internally of the shaft to a point on the periphery of the shaft remote from the chamber; and a lubricant conductor arranged peripherally of the shaft to return the lubricant to the chamber from the point on the periphery of the shaft at which the internal conductor discharges; of a collar for the shaft and having radiating ports with which the return conductor communicates, the radiating ports discharging into the chamber, whereby the discharge of lubricant by centrifugal action through the ports, creates a partial vacuum in the line including both the return and the internal conductors, to induce a substantially continuous circulation and re-circulation of lubricant from and to the chamber.

4. In a lubricant circulating system for shafts, the combination with a casing having a chamber; means to supply lubricant to the chamber; a rotary shaft, one end of which projects into the lubricant chamber said shaft having a normally horizontal axis; means supporting said chamber for adjustment about the shaft axis whereby said chamber will be disposed in any one of a number of positions within a range of substantially 150; means having an intake in the chamber to lead the lubricant from the chamber through the shaft and discharge it at the periphery of the shaft at a point remote from the chamber; and a lubricant conductor arranged spirally of the shaft, and extending from the point at which the lubricant is discharged at the periphery of the shaft, back towards the lubricant chamber; of a suction means communicating with the return end of the spiral conductor to create a partial vacuum in the spiral conductor for inducing a flow of lubricant from and to the lubricant chamber, and means to maintain the lubricant in the chamber at a substantially constant level with respect to the intake of the lubricating system irrespective of the angle to which the casing may be so adjusted about the axis of the shaft.

5. In a lubricant circulating system for shafts, the combination with a casing having a chamber; means to supply lubricant to the chamber; a rotary shaft, one end of which projects into the lubricant chamber said shaft having a normally horizontal axis; means supporting said chamber for adjustment about the shaft axis whereby said chamber will be disposed in any one of a number of positions within a range of substantially 150; means having an intake in the chamber to lead the lubricant from the chamber through the shaft and discharge it at the periphery of the shaft at a point remote from the chamber; and a lubricant conductor arranged spirally of the shaft, and extending from the point at which the lubricant is discharged at the periphery of the shaft, back towards the lubricant chamber; of a suction means communicating With the return end of the spiral conductor to create a partial vacuum in the spiral conductor for inducing a flow of lubricant from and to the lubricant chamber, the casing having a series of circularly arranged over-flow openings co-axial relatively to the shaft, to maintain the lubricant in the chamber at a substantially constant level with respect to the intake, irrespective of the angle to which the casing may be adjusted about the axis of the shaft.

6. A closed circuit lubricating means for shafts, including, in combination, with a casing having a lubricant reservoir chamber formed therein; means to supply lubricant to the chamber; and a rotary shaft journaled in the casing, one end of which shaft projects into the chamber; the shaft having a passage extending longitudinally thereof, from the chamber with which it communicates, and a duct connecting the passage with the periphery of the shaft; a lubricant conductor spirally encircling the shaft and with which the duct connects; a collar on that end of the rotary shaft projecting into the chamber, the collar having ports discharging into the chamber, and the collar also having a collection ring from which the ports radiate and with which the spiral conductor connects, to enable the partial vacuum created in the spiral conductor by the rapid rotation and centrifugal discharge of the lubricant from the radiating ports to induce a substantially continuous flow of lubricant from the open end of the passage, through the connecting duct and along the spiral conductor to the ports which discharge the lubricant into the chamber for re-circulation.

7. A lubricating system for a rotary shaft, having an oil intake at the inner end of the shaft; a passage extending longitudinally of the shaft from the oil intake; an oilreturning groove arranged peripherally of the shaft to return the oil back toward the inner end of the shaft; means to connect the said passage and oil return groove at a point remote from the inner end of the: shaft; a collar on the shaft having at least one radiating port formed therein, which communicates with the discharge end of the oil return groove and operating to create a partial vacuum in the groove by centrifugal and capillary action, on rotation of the shaft, to induce a flow of lubricant along the passage in one direction, and its return along the groove in the opposite direction, and prevent oil seepage along the periphery of the shaft toward the outer end.

8. A lubricating system comprising a rotary shaft member having an outer periphery and a bearing member having an inner periphery supporting the outer periphery of the shaft member; lubricant intake passage means for the flow of lubricant along the interior and axially of the rotary shaft member; radial lubricant passage means for the flow of lubricant from the axial passage means to the periphery of the shaft member and which by centrifugal action of the radial passage means is operative by suction to produce flow of lubricant from the axial intake passage means to said bearing member; the periphery of one of said members having a groove therein to provide for flow of lubricant from the radial passage means and along the bearing periphery; a collar fixed on said rotary shaft member, said collar having outwardly extending lubricant outlet means therein; said outlet means having inner and outer ends, said inner ends being in communication with said grooves, whereby to induce lubricant to flow through said grooves from said radial passage means in said shaft member to the outer ends of said outlet means in said collar.

9. In a motion picture apparatus a housing having Wet and dry sides; a drive shaft having opposite ends respectively terminating in said wet and dry sides; an elongate bearing also having opposite ends terminating in said wet and dry sides, respectively, and rotatably supporting said shaft in said housing; means for lubricating said bearing while preventing the escape of lubricant into said dry side, comprising lubricant supply passage means extending axially along the interior of said shaft, said supply passage means having an intake end communicating with the interior of the housing in said wet side and having an outlet end disposed towards the dry side of the lions ing, radial passage means extending outwardly from said outlet end and terminating in a discharge opening at the periphery of the shaft inwardly of and adjacent the end of the bearing in the dry side of the housing, the centrifugal action of said radial passage means inducing lubricant to flow from said wet side along the interior of said shaft to the discharge opening of the radial passage means; and centrifugal suction means of larger effective diameter than the shaft, and rotating with said shaft in the Wet side of the said housing for inducing said lubricant to 11 flow back along the periphery of the shaft to the wet side of said housing.

10. In a lubricating system, a lubricant supply, ,a shaft having lubricant passage means formed interiorlythereof and extending from adjacent the lubricant supply to a point remote from the supply to draw lubricant from the supply and discharge it at the periphery of the shaft at the remote point and a collar rotatable with the shaft .and located thereon adjacent said supply, said collar having outwardly extending lubricant jet conduit means communicating with the surface of the shaft to draw the lubricant from the supply through the passage means .and to supply all said lubricant to the surface ,of the shaft to provide for reverse flow along said surface back towards the collar for discharge through said jet means into the sup ly- I Referen c'es Citedin the file of this patent UNITED STATES PATENTS Heinrich May 25, 1926 1,787,428 Fekete Jan. 6, 1931 2,008,581 Dennison July 16, 1935 10 2;615,-533 Cliborn Oct. 28, 1952 FOREIGN PATENTS -.41'.7,-465 Germany Aug. 11, 1925 Germany July 25, 1933 

